Washing machine transmissions



ZJZUJHI O. J. VOSS WASHING MACHINE TRANSMISSIONS I Oct. 11, 1955 4 Sheets-Sheet 1 Filed Jan. 15, 1951 FIG. I.

INVENTORI OTTO J. Voss Oct. 11, 1955 o. J. voss 2,720,118

WASHING MACHINE TRANSMISSIONS Filed Jan. 15, 1951 4 Sheets-Sheet 2 OTTO J. Voss ATTORN F YS.

Oct. 11, 1955 o. J. voss WASHING MACHINE TRANSMISSIONS 4 Sheets-SW 5 Filed Jan. 15, 1951 INVENTOR. OTTO J. a

OSS

ATTORNEYS.

O. J. VOSS Oct. 11, 1955 WASHING MACHINE TRANSMISSIONS 4 Sheets-Sheet 4 Filed Jan. 15, 1951 INVENTOR. 4 OTTO J. 055 fiWda AT TORNE YS.

United States Patent WASHING MACHINE TRANSMISSIONS Otto J. Voss, Normandy, Mo., assignor to The Simmons National Bank, Pine Bluff, Ark., a corporation of the United States, as trustee Application January 15, 1951, Serial No. 206,055

9 Claims. c1. 74--s2 This invention relates generally to washing machine transmissions and particularly to mechanism for varying the stroke of the transmission and the speed of the Washing machine agitator.

In the usual washing machine wherein an agitator is rotated about a shaft first in one direction and then in the opposite direction, it is conventional to provide a socalled transmission for converting unidirectional rotary movement of a source of power into oscillatory movement of a pitman, rack or bow, and then to convert said oscillatory movement into rotary movement of the agitator shaft in opposite directions. One type of such transmission is disclosed in my co-pending application, Serial No. 110,319, filed August 15, 1949, now Patent No. 2,634,615.

The maximum rotational speed achieved by the agitator is dependent not only upon the rotational speed of the source of power and any gear reductions which may exist, but also upon the throw of the crank, which converts the rotational movement into oscillatory movement. The greater the throw of the crank, the higher will be the maximum rotational speed of the agitator, other variables remaining constant in any given mechanism. It has long been recognized that the optimum maximum rotational speed of the agitator is different for a coarse fabric than for a fine fabric laundry. Moreover it may at times be desirable in the process of laundering that the agitator speed of revolution be different in the early stages from the later stages of washing.

A variable speed motor has been tried for this purpose, and while the maximum peripheral speed of the agitator may thereby be varied, the amplitude of oscillation remains constant and results, at slow speeds, in tangling and knotting of the fabrics being laundered, with consequent reduction in the efficiency of the laundering operation. The ideal laundering condition involves a rather close corelation of amplitude and speed of the oscillation, whether fast or slow.

The object of the present invention generally stated is to provide a mechanism for varying the throw of the crank in a washing machine transmission.

Another object of the invention is to provide a mechanism of the character aforesaid, wherein the energy necessary to accomplish such variation in the throw of the crank is derived from the source of power which drives the transmission.

A more specific object of the invention is to provide a washing machine transmission wherein the throw of the crank may be changed from a position of low eccentricity to a position of high eccentricity without interfering with the continued operation of the device.

In accordance with the present invention, a washing machine transmission having a crank for imparting oscillatory movement to another member is provided with means for varying the effective eccentricity of the crank. Such means may take the form of a crank on a crank with auxiliary means for locking the respective cranks in a plurality of positions relative to each other; or such means may take the form of a crank arm which is adjustable radially with respect to its axis of rotation, together with auxiliary means for locking said crank arm in a plurality of radial positions. The invention also contemplates the provision of means for unlocking the adjustable crank, which means may be actuated from the exterior of the transmission and is preferably so disposed that the unlocking occurs at a position in the revolution of the crank where the driving force and the reaction of the load constitute a couple Whose tendency is to move the crank in the direction of desired variation.

Three embodiments of the invention are shown in the accompanying drawings, in which:

Figure 1 is a plan view of a washing machine transmission embodying the present invention;

Figures 2, 3, and 4 are views corresponding to Figure 1, but showing the worm wheel and adjunct parts of the transmission in different relative positions;

Figure 5 is a left end view of the mechanism shown in Figure 1 together with shifting mechanism therefor and an enclosure, the latter being shown in section to reveal the relationship of the elements;

Figure 6 is a plan view of a shifting mechanism shown in the upper section of Figure 5 and diagrammatically correlated with the parts shown in Figure 1;

Figure 7 is a sectional view taken along line 7--7 of Figure 3;

Figure 8 is a perspective view of the shifter plate element of the apparatus shown in Figures 1-5, inclusive;

Figure 9 is a view corresponding to the left end of Figure 1, but showing a modified form of the invention;

Figures 10 and 11 are views corresponding to Figure 9, but showing the various parts thereof in different relative positions;

Figure 12 is a sectional view taken along line 12-12 of Figure 9;

Figure 13 is a sectional view taken along line 13--13 of Figure 9;

Figure 14 is a perspective view of a cross-head element embodied in the device shown in Figures 9-13, inclusive;

Figure 15 is a view corresponding to the left end of Figure 1, but showing a further embodiment of the invention;

Figure 16 is a sectional view taken along line 1616 of Figure 15;

Figures 17 and 18 are views corresponding to Figure 15, but showing the parts thereof in different relative positions;

Figure 19 is a sectional view taken along line 1919 of Figure 15, but showing some of the parts in a different position;

Figure 20 is a sectional view taken along line 2020 of Figure 15;

Figure 21 is a view corresponding to Figure 20, but showing the parts thereof in the relative positions shown in plan by Figure 17;

Figure 22 is a perspective view of a reversible crank element utilized in the embodiment shown in Figures 15-21, inclusive; and

Figure 23 is a perspective view of a latch element utilized in the embodiment shown in Figures 1521, inclusive.

In the embodiment shown in Figures 1-5, inclusive, the stroke-changing apparatus of the present invention is illustrated in connection with an oscillating mechanism of the character disclosed in my said Patent No. 2,634,615, but it will be understood that other types of transmission such as the familiar rack and pinion or the familiar pitman and crank may be employed.

In the embodiment illustrated, a suitable source of power (not shown) applies rotational force to a worm 1 which is engaged with a worm wheel 2 in the, customary manner.

Mounted upon one face of the worm Wheel 2 is a shifterpla'te 3 movable abouta pivotpin 4 between the extreme positions illustrated in Figures 1 and 3.

The pivotpin-4'i's-secured in the wheel 2. Upstanding from which theeccentricity of the-crank pinS from the center of worm wheel. 2 is considerably greater than the eccentricity thereof in the position .shown in Figure 3. Accordingly, the stroke of bow 6.is changed from long to short when the plate 3 is moved about its pivot 4 from the position shownin=Fi'gure 1' tothat shown in Figure 3.

In order to lock the plate 3 in either of the extreme positions shown in Figures 1 and 3, a suitable latching mechanism is mounted on worm wheel 2. In the embodiment shown, the latching mechanism is provided by .a lug 7 on; plate 3 oneither side of which a detent 8 is adapted to engage, as shown in Figures 1 and 3. The

detent 8 is. moved out of engagement with the lug 7 to the position shown in Figure 2 in order to permit the plate 3 to move about its pivot 4 to vary-the eccentricity of the crank arm 5. Movement of the plate 3 in a counterclockwise direction about pivot 4 beyond the position shown in Figure 1 is precluded by a suitable stop 9 also mounted'upon the worm-wheel, while movement of the, plate 3'in a clockwise direction about pivot 4 beyond the position shown in Figure 3 is limited by a stop 10. Both stops 9 and 10 are mounted upon the face of worm wheel .2. 'When one side of the lug 7 is engaged by detent 8, the other side thereof is engaged by one or the otherof stops 9 and 10. Thus the plate 3 is locked in eitherof two running positions, the one shown in Figure l. where the eccentricity of crank pin 5 is great, and the other shown in Figure 3 where the eccentricity of crank pin 5 is small.

In order to release detent 8 from engagement with lug 7, an actuator 11 is pivotally connected with worm wheel 2 by a pin 12. One end of the actuator 11 is pivoted at 13 to the detent 8, while the opposite end 14 of the actuator is arranged to project (when the detent 8 is engaged with lug 7) into the path of one or the other of abutments 15 and 16. The abutments 15 and 16 are mounted upon a fixed part of the apparatus such as case 17 but are arrangedto be selectively moved into and out of the path followed by end 14 of actuator 11 as the latter rotates about the axis of worm wheel 2.

A spring 18 carried by worm wheel 2 biases detent 8 toward the axis of worm wheel 2 and into the position shown in Figures 1 and 3. Accordingly,movement of the actuator 11. from the position shown in Figure 1 or Figure 3 to the position shown in Figure 2 is resisted by spring-18.

In the embodiment shown, the abutments Hand 16 are spring-biased intoaposition outside the orbit of actuatorend 14. Asshown in Figure 5, the abutments 15 and 16 are in the form of thimbles mounted-in-telescopic relation upon pins 19and 20, the latter being suitably secured within case 17. Between'the'inner ends of the abutments 15 and 16 and the upper ends of pins 19 and 20 respectively, coil'springs 21:are interposed in order to biasthe-abutments- 15 and 16.11pwardly and thus permit the tail 14 of actuator 11 to pass freely thereoeneath during normaloperation. In order'to accomplish the movement of plate 3 between the positions shown in Figures 1 and 3,'one or the other of abutments 15 and 16. may be pressed downwardly againstthe action of spring 21 into aposition whereit is atfthe same elevation as the tail 14 of actuator 11,.in which position'the-abutmentswill engage the tail .14.:as the latter travels about'the axis of worm wheel 2.

'Any suitabledevice :for transmitting-atone from the exterior of the case to abutment 15, may beprovided., '..In the embodiment shown, a lever 22 is arranged so that end 23 thereof engages the upper surface of abutment 15. The opposite end of lever 22 is loosely mounted upon a pin 24 and biased by spring 25 into engagement with a fixed seat 26 constituting an integral part of cover 27.

Similarly, a lever 32 has its end 33 in engagement with the upper end of abutment 16 and has its opposite end mounted loosely on a pin 34 and biased by .a spring corresponding to spring 25 against a. seat 36 which is'an integral part of cover 27.

The spring 25 and its companion mounted upon pin 34 is of greater stiifness than the springs 21 so that the application of a downward force upon levers 22 or 32 as the case may be, between the ends thereof will result in a downward movement of ends 23 or 33, as the case may be, in preference to downward movement of the ends which are seated upon seats 26 or'36, as the-case may be. If, however, downward-movement of theabutment 15 is fouledas by the happenstance that the tail 14 of actuator 11 may be in position therebeneath when the lever 22 is pressed downwardly, spring 25 does yield to permit that end of the lever to losecontact with'its seat 26.

In order to apply the downward'force to levers 22 or 32 and to initiate such force from the exterior of the enclosed transmission, a rocker shaft 40 having a handle 41 on the exterior of cover 27 passes through the cover and is provided on the interior thereof with a crank 42 having a part 43 arranged to make engagement with-the upper side of a flange 44 secured tolever 22. Similarly a crank 45 has a part 46 arranged to make engagement with the'upper side of a flange 47 secured to lever 32. Accordingly, rotation of. rocker shaft 40 in the clockwise direction shown in Figure 5 movescrank 42. from the position shown in dotted lines in Figure 5 to the position shown in full lines therein, thus pressing lever 22 downwardly from the position shown in dotted lines to the position shown in full lines in Figure 5, and thus pressing abutment 15 downwardly into the full line position.

Similarly, rotation of rocker arm 40 in the counterclockwise direction as seen in Figure 5, moves crank 45 and lever 32 in a comparable manner but'in the opposite sense, to press abutment 16 downwardly into position where it will engage tail 14.

The cranks 42 and 45 are respectively provided with terminal parts 48 and 49 for engagement with a moving part of the mechanism to restore rocker arm: 40 and its adjunct parts to their-normal position in a manner to be later described.

In the operation of the device, assuming the parts tozbe in the position shown in Figure 1 where crank pin Sisat its greater eccentricity, the rocker arm 40 is rotated soias to depress lever 22 and abutment 15 into the'position shown in full lines in Figure 5. In this position the abutment 15 lies in the path of the tail 14 of actuatorll. Accordingly, when (during rotation of wheel 2) the actuator makes engagement with the abutment 15, continued rotational'movement of worm wheel 2 in the direction indicated by the arrow in Figure 1 moves actuator 11 in a clockwise direction about its pivot pin 12, thus lifting detent 8 out of engagement with the lower shoulder of lug 7. This operation occurs within the space of .a few degrees counterclockwise rotational movement ofworm wheel 2 beyond the position shown in Figure 1. In this quadrant the driving force imparted by worm wheel.'2 throughpin 4, andthe resistance imposed by how 6, tend to move plate .3 in a clockwise direction about its pivot 4. Continued movement of the'apparatus in thesame direction results in a shifting of plate '3 and crank pin 5 from the position shownin Figure l to the position shown in Figure 2, andthence' to the position shown in Figure 3, within less than one-half revolution of worm wheel 2. The movement of plate 3 from 'theposition shownin Figure l-to the position shown in Figure 3 is thuscompleted before the driving and reaction forces begin to "operatetin-a direction which tends to move plate 3 in the counterclockwise direction about its pivot 4. Thus the "stroke of how 6 is shortened; At the shortened stroke, in the embodiment shown, the oscillation of the agitator has "-an amplitude on the order of ninety degrees.

"By changing the stroke of the bow, the amplitude of agitator oscillation may bechanged to 205, in the em- "bodiment shown, with corresponding increase in peripheral speed. When it is desired to increase the stroke of how *6, rocker shaft 40 is moved in the clockwise direction, as seen in Figure depressing lever 32 and abutment 16 so that the latter lies in the path of the tail 14 of actuator 11,and the detent 8 is thereby released from engagement with lug 7 inthe identical manner described above in connection withabutment 15, but at a different quadrant of "rotation of wormwheel 2. The position of release in this case isa few degrees counterclockwise beyond the position shown *inFigure 3. In this quadrant, the driving forces and'reaction are such as to tend to move plate 3 in a counterclockwise direction-about its pivot4, and accord- =ingly, when the plate 3is unlocked, at this position in its orbit, plate 3 and crank pin 5 move from the position of low eccentricity shown inFigure 3 to the. position of ggreat eccentricity shown in Figure 1.

In the embodiment shown, the movement of rocker shaft 40 to cause engagement of tail 14at abutment 15 isto an extent such that crank 42 iscarried to a position slightly over center where the forces exerted by springs 21 and 25 tend to resist backward movement of the crank -42 to its normal position. Thus, when the position of rocker shaft 40 is changed from the normal position shown in dotted lines in Figure 5 to the actuating position shown in full lines, the parts remain in the latter position until a force is applied to overcome the oppositely acting force of said springs.

Similarly, 'but inthe opposite sense, whencrank 45 is moved from its neutral position to the shifting position, acomparable over-center action takes place, retaining the =partsin those positions until subsequent positive action occurs. "This arrangement of parts assures that if the shifting of plate 3 between the positions of greater and lesser eccentricity doesnot occur during the time which manual effort continues to be applied to handle 41, shifting will-occur on the next revolution of worm wheel 2. This arrangement necessitates that means for positively driving the rocker shaft 40 out of shifting position be provided, and such will now be described.

When thecrank pin 5 is in the position of low eccentricity shown in Figure 3, and rocker arm 40 is in the position which actuated movement from high eccentricity 'to low eccentricity positions of crank pin 5, part 49 of crank 45 is inposition to be engaged by a stud 50 (whose orbit at this time is indicated by the dot-dash circle of greater diameter shown in Figure 6) on crank pin 5. When engagement between stud 50 and part 49 occurs during movement of the worm wheel 2, part 49 and its adjunct parts, crank 45 and rocker shaft- 40, are moved back into their normal position where both abutment 15 and abutment 16 are removed from thepath' of tail 14. .In like manner, when crank 42 is in the position shown in full lines in Figure 5, part 48 thereof is disposed in .the pathof stud 50 and engagement between those parts resultsinrestoration of rocker shaft 40 to its normal "positiontshown in dotted lines in Figure 5. It will be (observed from Figure 6 that parts 48 and49 are situated onopposite sides of the axis of worm wheel 2 so that the engagement of those parts by stud 50 results in moving the same in opposite directions.

Referring now to Figures 914 inclusive for a further embodiment, the worm wheel 2 is provided with a pair of guides *51 and 52 between which is slidably received a I cross-head 53having a crank pin 54 mounted thereon and sli dable therewith between the position of great eccentricity shown in Figure 9 and th position of low eccentricity shown in fiill'linesin Figure 11.

Mounted on the face of worm wheel'2 and inslidablerelation within'guide 51 is a detent 55 arrangedtoengage a recess '56 in one edge of cross-head 53thus to lock the latter in the positionwhere crankj pin54 is at its "greatest eccentricity. Also mounted on the face of worm wheel-2 is an actuator57 arranged for pivotal movementabout pin 58. 1 One end of the actuator57 is connected to detent 55 at pin 59- while the opposite end 60 of theactuator57 is arranged to project into a position'where itwill beengagedby abutment 61. In normal operation/the abutment-61 iselevated out of 'the path of tail"60of=acu- *ator '57, "but when it is desired to move'the crank pin54 from the -position of higheccentricity shown in"F igure-9 tothe position of low eccentricity shown irf-Figuredlfthe abutment 61 is depressed into the path of thetail"60 of -actuator57. When the actuator "57'engages the "abutment 61 during rotation of the worm whee12 in 'thecounterclockwise direction as seen in 'Figure"9, the actuator 57 is lifted out of engagement with recess-"56, suchbeing against the tension'ofa spring 62. 'The:cross-head"53"is thereupon free toslide diametrically of worm wheel2. The abutment-61 is so located thatthe cross-head53 is thus unlocked as it enters the northwest quadrant of rotation (as seen in Figure 9) wherein the reactionofthe load on crank pin'54 tends to reduce the eccentricity thereof. In order to supplement the inherent forces inmoving thecross-head53 from the position of higheccentricity to the position of low eccentricity, the abutment 61 is preferably arranged to engage a cam surface63 ontheendof 'cross head 53 and thus, during continued rotation'of the worm wheel 2, to cam cross-head 53 in a direction such that crankpin 54 moves toward the axis of rotation' of worm wheel 2. The-abutment 61 is of such circumferential extent that tail 60 of actuator 57 does not losecontact therewith until cam surface 63 has *been in engagement with the abutment-61 for a time sufficient to'move crosshead53 beyond a position where detent -55would'reengagerecess' 56.

On the opposite side of cross-head 53 a detent55"is provided for engagement with a recess 56' and the detent is adapted to be released by movement of an actuator57' upon engagement of the latter by a movable abutment 61 in order to initiate movement of the cross-head53 from the position of low eccentricity to theposition' of high eccentricity. The primed reference characters denote parts corresponding in structure and function to "those already described but connote the parts which areelfective to increase the eccentricity of crank pin54.

The movable abutments 61 and61' are each provided with a shank 64 extending through the'case andterrninating in a handle or knob 65 which is accessiblefor manipulation. A spring 66 continuously urges the movable abutment into a position where it is elevated above the orbit of tail 60 of actuator'57. In order to avoid the possibility that by the abutment 61 remaining depressed after cross- -head 53 has moved to the position shown in Figure 11 and would thus be in position to foul against cam surface 63, the leading edge of the abutment 61 is chamfered asshown at 67 so that upon such engagement of the cam surface 63' therewith, the abutment 61 will be lifted against any manual effort tending to hold the button -65 depressed. The abutment 61 is similarly chamfered to preventfouling.

In order to avoid the possibility that the button 65 be depressed so that the abutment 61 is moved into the path of cam surface 63 without first releasing detent 55, the abutment 61 is made of greater circumferential extent than the distance between tail 60 and cam surface 63. Accordingly, if the button 65 be depressed at the instant that the cam surface 63 is in the position shown in Figure 9 (but with the detent 55 engaged in the recess 66, and the tail60 of actuator 57 projecting outwardly beyond the position shown) the abutment 61 will be prevented'from movement into the position shown in full lines in Figure 12; the bottom surface of the abutment 61 will engage the top surface of tail 60 and be, thereby, held up until cam surface 63 is in position beneath the abutment and the possibility of fouling is eliminated. After the parts 60 and 63 have passed from beneath the abutment 61, it

may be depressed into the position shown in full lines in Figure 12, where it will be ready to engage tail 60 and release detent 55 upon the next revolution.

The abutment 61 which initiates movement of the cross head from the position of low eccentricity to the position of high eccentricity is constructed in like manner to abutment 60 but is situated in the southwest quadrant, as seen in Figures 9, 10, and 11, as in this quadrant the reaction exerted by the load is tending to pull crank pin 54 radially outward.

Accordingly, with the device operating with the crank pin 54 in the position of high eccentricity as shown in Figure 9, depression of abutment 61 initiates movement of the cross-head toward a position of lower eccentricity for crank pin 54. Conversely, with the device operating with the crank pin in the position of low eccentricity, depression of abutment 61 initiates movement of the parts toward the position whereat crank 54 is of greater eccentricity.

Referring now to Figures l-23 inclusive for a further embodiment of the invention, the worm wheel 2 is provided with an eccentric bearing 70 within which is received a stud 71 in freely rotatable relation. The stud 71 is secured to a crank arm 72 having a crank pin 73 at its one extremity. The stud 71 is rotatable within bearing 70 between the position shown in Figure where crank pin 73 is at a greater eccentricity to the position shown in Figure 18 Where crank pin 73 is at a low eccentricity.

In order to latch the crank 72 in either selected position of eccentricity, the face of worm wheel 2 is provided with a latch 74 of the character shown in Figure 23. The latch 74 is suitably secured to the face of the worm wheel as by rivets 75. As clearly shown in Figure 23, the latch 74 has a pair of side bars 76 which bend upwardly from the portion thereof secured at rivets 75. The latch 74 is provided with a cam surface 77 and thereadjacent with a pair of upstanding lips 78. The lips 78 are arranged to make locking engagement with the edges 79 of crank 72. In normal position of the latch 74, the lips 78 are held in engagement with the edges 79 by the resiliency of side arms 76, but the later may be flexed so as to move the lips 78 downwardly and thus release the edges 79. In order to accommodate the latch 74 in such downward movement, the face of worm wheel 2 may be recessed as shown at 80.

As in the previous embodiments, crank pin 73 is adapted to be connected with a pitman or bow member for converting the rotational movement of worm wheel 2 into oscillatory movement of the washing machine agitator. In this embodiment the pitrnan or bow member 81 is provided with a saddle 82 hinged to the bow member at 83 and having a pair of lobes 84 depending alongside the bow member and normally resting upon the upper edges of lips 78. If desired, the saddle 82 may be spring-biased downwardly into firm engagement with said edges, but normally the bias of gravity is suflicient for the purpose. As shown in Figure 19, when lips 7 8 of latch 74 release the edges 79 of crank 72, lobes 82 engage said edges 79, and during such time prevent rotational movement of crank 72 relative to member 81.

In order to release the interlocking engagement between crank 72 and latch 74, any suitable actuating device manipulatable from the exterior of the transmission case may be provided, but the actuating device must be so located as to effect such release at a position when the pitman 81 is aligned with the radius of Worm wheel 2 on which stud 71 is centered. In the embodiment shown, a rock shaft 85 extends through the case of the transmission and terminates in a cam 86 disposed for engagement with the portion 77 of latch 74. The cam 86 when rotated in the clockwise direction from the position shown in dotted lines to the position shown in full lines in Figure l9 depresses end 77 of latch 74 and thus releases lips 78 from the edges 7 9 of crank 72. Concurrently, the lobes 82 drop and interlock member 81 with the crank 72 as shown in Figure 19. The crank 72 is thus freed to rotate relative to worm wheel 2 about stud 71, and as it rotates from the position shown in Figure 15 to the position shown in Figure 18, the direction of throw of crank 72 relative to stud 71 will have changed During this movement, lips 78 are depressed below crank 72 so that the former pass under the latter, as shown in Figure 21. When the parts become re-aligned at 180 displacement from the releasing position, latch 74 springs back into a position whereat lips 78 engage the edges 79 and at the same time lobes 82 are forced upwardly out of engagement with edges 79, thus freeing crank 72 for rotational movement relative to member 81, and restraining it against rotational movement relative to worm wheel 2.

Irrespective of Whether crank 72 is in the position of greater eccentricity or in the position of low eccentricity, release of latch 74 upon engagement with the edges 79 of crank 72 will permit the operating forces within the transmission to effect a reversal of the position of crank 72 during 180 rotation of worm wheel 2 from the position at which the latch was released.

From the foregoing description, those skilled in the art should readily understand that the invention accomplishes its objects and provides a transmission mechanism suitable for use upon washing machines wherein the maximum speed of rotation of the agitator may be varied between a high and a low value by varying the throw of the crank arm which drives the agitator. Such variation in the throw of the crank arm is accomplishable during continued operation of the mechanism and selectivity in either direction, as well as to accomplish the movement of the parts between the respective positions without the application of forces other than those already at work in the mechanism. In each of the three embodiments disclosed hereinbefore, the only manual effort required to be exerted to effect a shift from either position to the other is the movement of an abutment member into position where it will engage and release a locking device which, after the shift has been accomplished, resumes a locking relationship with the other parts.

While three embodiments of the invention have been disclosed in detail, it is not to be understood that the invention is limited to those embodiments, but that the same are merely illustrative of different ways of applying the principles of the invention. It is realized that many variations of the precise mechanism disclosed will present themselves to those skilled in the art, without departing from the spirit of the invention, and consequently, it is to be distinctly understood that the invention is not limited to the detailed aspects of the foregoing disclosures, save as indicated in the appended claims.

Having thus described the invention, what is claimed and desired to be secured by Letters Patent is:

1. In a washing machine transmission having a unidirectionally rotatable driving member, an agitator shaft and means including a crank on said driving member for transmitting motion from the driving member to said shaft; the combination of a crankpin supporting member mounted on said driving member for movement relative thereto, locking means mounted on said driving member, said locking means having a latch part movable into locking engagement with the crankpin supporting member to lock the latter in a selected one of a plurality of positions on said driving member and having an actuating part projecting beyond the orbit of the crankpin supporting member, and a manually controlled element mounted clear of 9 the driving member for movement into the orbit of said projecting part to actuate the latch part and release the crankpin supporting member for movement relative to the driving member.

2. The combination of claim 1 wherein said crankpin supporting member is connected to said driving member for relative movement about an axis parallel with but eccentric to the axis of rotation of said driving member.

3. The combination of claim 1 wherein said crankpin supporting member is connected to said driving member for sliding movement in a radial direction relative to the axis of rotation of said driving member.

4. The combination of claim 1 wherein the crankpin supporting member is pivoted at one end to said driving member and is pivoted at its opposite end to a pitman, and the locking means comprises a latch carried by the rotatable driving member and engageable with said crankpin supporting member at positions of 180 displacement about said pivotal connection with said driving member.

5. The combination of claim 1 wherein the crankpin supporting member is pivoted at one end to said driving member and is pivoted at its opposite end to a pitman, and the locking means comprises a latch carried by the rotatable member and engageable with said crankpin supporting member at positions of 180 displacement about said pivotal connection with said driving member, and a second latch carried by said pitman for interlocking engagement wtih said crankpin supporting member when said first mentioned latch is released.

6. In a washing machine transmission having a unidirectionally rotatable driving member, an agitator shaft and means including a crank on said member for trans mitting motion from the driving member to said shaft; the combination of a crankpin supporting member mounted on said driving member for movement between crank-in and crank-out positions relative to the axis of the driving member, said crankpin supported member being subjected to forces tending to move it from the crank-in position during rotation of the driving member over a predetermined arc, locking means mounted on the driving member including a latch part biased into locking engagement with the crankpin supporting member to lock the latter in its crank-in position and including an actuating part projecting beyond the orbit of said crankpin supporting member, and a manually controlled element mounted clear of the driving member for movement into and out of the orbit of said actuating part, said control element being positioned relative to the orbit of said actuating part to engage said part when the driving member swings through said predetermined arc.

7. In a Washing machine transmission having a unidirectionally rotatable driving member, an agitator shaft, and means including a crank on said member for transmitting motion from said member to said shaft; the combination of means mounting said crank on said member for movement relative thereto, means mounted on said member for locking said crank in a selected one of a plurality of positions on said member, said locking means comprising a detent movable into and out of interlocking engagement with said crank, a spring biasing said detent toward engaged position, an actuator movable to lift said detent out of engaged position, and a. manually controlled abutment mounted independently of said driving member and selectively movable into and out of the path of said actuator, said abutment being arranged to move said actuator when said parts engage during rotation of said member.

8. In a washing machine transmission having a unidirectionally rotatable driving member, an agitator shaft, and means including a crank on said member for transmitting motion from said member to said shaft; means mounting said crank on said driving member for movement relative thereto, said crank being pivoted eccentrically to said driving member and said crank being pivotally connected to a pitman in a position spaced from said first pivot, means for limiting the amplitude of movement of said crank about said first pivot, said crank having a lug projecting therefrom, locking means mounted on said driving member and engageable selectively with opposite sides of said lug when said crank is at the respective eX- tremes of its amplitude of movement, said locking means having a part projecting beyond the orbit of the crank, and manually controlled means mounted inwardly of said driving member and movable into the orbit of said projecting part of said locking means to release the latter during rotation of said driving member.

9. The combination of claim 8 wherein said locking means comprises an actuator pivoted to said driving member and to said locking means and having an outwardly projecting tail, and a pair of abutments mounted in spaced relationship about the orbit of said tail, said abutments being normally clear of said orbit but selectively movable into said orbit.

References Cited in the file of this patent UNITED STATES PATENTS 520,157 Davids May 22, 1894 1,829,555 Criner Oct. 27, 1931 1,847,048 Orr Feb. 23, 1932 1,856,268 Schmiedeknecht May 3, 1932 

